EP1321312B1 - Lagervorrichtung für ein Antriebsrad eines Fahrzeuges - Google Patents

Lagervorrichtung für ein Antriebsrad eines Fahrzeuges Download PDF

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Publication number
EP1321312B1
EP1321312B1 EP02258836A EP02258836A EP1321312B1 EP 1321312 B1 EP1321312 B1 EP 1321312B1 EP 02258836 A EP02258836 A EP 02258836A EP 02258836 A EP02258836 A EP 02258836A EP 1321312 B1 EP1321312 B1 EP 1321312B1
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EP
European Patent Office
Prior art keywords
hub wheel
joint member
outer joint
wheel
bearing apparatus
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
EP02258836A
Other languages
English (en)
French (fr)
Other versions
EP1321312A3 (de
EP1321312A2 (de
Inventor
Masahiro Ozawa
Eiji Tajima
Mitsuru Umekida
Hiroyuki Ogura
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
NTN Corp
Original Assignee
NTN Corp
NTN Toyo Bearing Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Priority claimed from JP2001389630A external-priority patent/JP4005354B2/ja
Priority claimed from JP2002000546A external-priority patent/JP4071965B2/ja
Priority claimed from JP2002002673A external-priority patent/JP2003206947A/ja
Application filed by NTN Corp, NTN Toyo Bearing Co Ltd filed Critical NTN Corp
Publication of EP1321312A2 publication Critical patent/EP1321312A2/de
Publication of EP1321312A3 publication Critical patent/EP1321312A3/de
Application granted granted Critical
Publication of EP1321312B1 publication Critical patent/EP1321312B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B35/00—Axle units; Parts thereof ; Arrangements for lubrication of axles
    • B60B35/12—Torque-transmitting axles
    • B60B35/18—Arrangement of bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C35/00—Rigid support of bearing units; Housings, e.g. caps, covers
    • F16C35/04—Rigid support of bearing units; Housings, e.g. caps, covers in the case of ball or roller bearings
    • F16C35/06—Mounting or dismounting of ball or roller bearings; Fixing them onto shaft or in housing
    • F16C35/063—Fixing them on the shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60B—VEHICLE WHEELS; CASTORS; AXLES FOR WHEELS OR CASTORS; INCREASING WHEEL ADHESION
    • B60B27/00—Hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/186—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with three raceways provided integrally on parts other than race rings, e.g. third generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/14—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load
    • F16C19/18—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls
    • F16C19/181—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact
    • F16C19/183—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles
    • F16C19/184—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement
    • F16C19/187—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for both radial and axial load with two or more rows of balls with angular contact with two rows at opposite angles in O-arrangement with all four raceways integrated on parts other than race rings, e.g. fourth generation hubs
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C43/00—Assembling bearings
    • F16C43/04—Assembling rolling-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/52—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions
    • F16C19/527—Bearings with rolling contact, for exclusively rotary movement with devices affected by abnormal or undesired conditions related to vibration and noise
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2326/00—Articles relating to transporting
    • F16C2326/01—Parts of vehicles in general
    • F16C2326/02—Wheel hubs or castors
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/30—Parts of ball or roller bearings
    • F16C33/58—Raceways; Race rings
    • F16C33/60—Raceways; Race rings divided or split, e.g. comprising two juxtaposed rings
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/86—Optimisation of rolling resistance, e.g. weight reduction 

Definitions

  • the present invention relates to a bearing apparatus for a driving wheel of vehicle and more particularly to a bearing apparatus for a driving wheel of vehicle in which a hub wheel, a constant velocity universal joint and a double row rolling bearing are assembled as a unit.
  • the driving wheels such as rear wheels of a rear wheel drive vehicle, front wheels of a front wheel drive vehicle and all wheels of a 4WD (4 wheel Drive) vehicle are supported by a suspension system via a bearing apparatus for a driving wheel.
  • a bearing apparatus for a driving wheel In recent years, it has a tendency to assemble the hub wheel, the constant velocity universal joint and the double row rolling bearing as a unit in order to reduce the weight and the size of the bearing apparatus for a driving wheel.
  • Fig. 8 is a longitudinal cross-section view of a bearing apparatus for a driving wheel of vehicle of the prior art in which a hub wheel 50, a double row rolling bearing 60 and a constant velocity universal joint 70 are assembled as a unit.
  • the hub wheel 50 is formed integrally with a wheel mounting flange 51 for mounting a wheel (not shown) thereon and hub bolts 52 for securing the wheel are equidistantly arranged along the periphery of the flange 51.
  • the double row rolling bearing 60 comprises an outer member 61, an inner member 62 and double row rolling elements 63 and 63 and the outer member 61 has a flange 64 integrally formed therewith to be mounted on a body of vehicle (not shown) and double row outer raceway surfaces 61a and 61a formed on the inner surface thereof.
  • the inner member 62 comprises the hub wheel 50 and an outer joint member 71.
  • the inner member 62 is formed with double row inner raceway surfaces 50a and 71a arranged respectively opposite to the outer raceway surfaces 61a and 61a of the outer member 61.
  • the inner raceway surface 50a is formed on the outer circumferential surface of the hub wheel 50 and the other raceway surface 71a is formed on the outer circumferential surface of the outer joint member 71 of the constant velocity universal joint 70.
  • the double row rolling elements 63 and 63 are arranged between the outer raceway surfaces 61a and 61a and the inner raceway surfaces 50a and 71a and rotatably held therein by cages 65 and 65. Seals 66 and 67 are arranged at the ends of the double row rolling bearing in order to prevent leak of grease contained within the bearing and also to prevent incoming of rain water or dusts.
  • the constant velocity universal joint 70 comprises the outer joint member 71, a joint inner ring, a cage and a torque transmission balls (not shown).
  • the outer joint member 71 has a cup shaped mouth portion 72, a shoulder 74 forming the bottom of the mouth portion 72, a shaft portion 73 axially extending from the shoulder 74, and axially extending curved track grooves 72a formed on the inner surface of the mouth portion 72.
  • the hub wheel 50 is formed with hardened irregular portion 53 on the inner circumferential surface thereof and has a cylindrical spigot portion 50b at the end thereof.
  • the hub wheel 50 and the outer joint member 71 are mutually connected by fitting the shaft portion 73 of the outer joint member 71 into the hub wheel 50 and then by radially outwardly expanding the fitting portion of the outer joint member 71 so that causing plastic deformation of the outer joint member 71 with making the hardened irregular portion 53 to bite into the outer circumferential surface at the fitting portion of the outer joint member71 (see Japanese Laid-Open Patent Publication No. 18605/2001 ).
  • connection via the plastic deformation can prevent loosening and abrasion of the fitted portion and thus can improve the durability and the driving stability.
  • connection via the plastic deformation has both functions of torque transmission and connection of the hub wheel and the outer joint member, it is possible to eliminate securing means such as fastening nuts and to achieve reduction of the weight and size of the apparatus.
  • EP-A-1218461 discloses a wheel bearing device formed by a hub ring, a bearing and a one-piece constant velocity universal joint.
  • the joint includes a stem that is received in a bore in the hub ring, with the bore being formed with an irregular portion treated by hardening. A portion of the stem of lower hardness than the irregular portion is expanded to bite into the irregular portion.
  • US-A-2001/0016520 discloses a drive wheel bearing assembly formed by a hub ring, a wheel bearing and a fixed type constant velocity universal joint. The joint includes a stem received in a bore of the hub ring with mating serrations between the parts and a connecting bolt.
  • an object of the present invention to provide a bearing apparatus for a driving wheel of vehicle which can reduce the weight and the size of the apparatus due to the connection of the hub wheel and the outer joint member via plastic deformation as well as the generation of excessive stress and abrasion and also can improve the durability and thus the lifetime of the apparatus.
  • a bearing apparatus for a driving wheel of vehicle comprising a hub wheel formed with a wheel mounting flange at one end thereof, a constant velocity universal joint including an outer joint member integrally formed with a mouth portion, a shoulder portion forming the bottom of the mouth portion and a shaft portion axially extending from the shoulder portion, and a double row rolling bearing for rotatably supporting a vehicle wheel relative to a body of a vehicle, the hub wheel, the constant velocity universal joint and the double row rolling bearing being assembled as a unit, one of the inner raceway surfaces being formed on the outer circumferential surface of the hub wheel, the other of the inner raceway surfaces being formed on the outer circumferential surface of the outer joint member, the hub wheel and the outer joint member being fitted each other with one end surface being abutted against the shoulder of the outer joint member, the inner circumferential surface at the fitting portion of the hub wheel being formed with a hardened irregular portion, the hub wheel and the outer joint member being integrally connected via plastic deformation of the outer joint member
  • connection via plastic deformation defined in claim 1 it is possible to reduce the weight and the size of the apparatus and also possible to suppress the generation of excessive stress at the shaft portion and the its end and thus to improve the durability of the bearing apparatus for a driving wheel.
  • the hub wheel is formed with a cylindrical spigot portion axially extending from the inner raceway surface, and wherein a hardened layer is formed on the outer circumferential surface of the hub wheel in a region including the spigot portion and extending from the inner raceway surface to one end surface of the hub wheel.
  • grease is arranged between the abutted surfaces of the end of the hub wheel and the shoulder of the outer joint member.
  • This structure enables to suppress abrasion of the abutted portion, twist of the shaft portion of the outer joint member, and generation of noise of relative slippage between the outer joint member and the hub wheel, so-called stick-slip noise.
  • a grease well is formed on the end surface of the hub wheel. This enables to further suppress the generation of abrasion and stick-slip noise.
  • the radial clearance between the spigot portion of the hub wheel and the shaft portion of the outer joint member is set less than 0.5 mm. This enables to receive the repeating bending loads on a cylindrical surface and thus to suppress the deformation of the spigot portion. Accordingly the durability of the apparatus is remarkably improved.
  • the connected portion via plastic deformation at a place axially outward from the line of action of the double row rolling bearing, it is possible to suppress the bending moment from acting on the plastically deformed connected portion. Accordingly since this connected portion has both functions of torque transmitting means and of connecting means of the hub wheel and the outer joint member, it is possible to obtain a desired lifetime of the apparatus.
  • the hub wheel and the outer joint member are mutually spigot-fitted, and wherein the spigot-fitted portion is arranged on the line of action of the double row rolling bearing.
  • the hub wheel is extended outward from the wheel mounting flange to form a wheel piloting portion, and wherein the connected portion via plastic deformation is arranged at a region from the end face of the wheel piloting portion to the wheel mounting flange. This enables to suppress the bending moment from acting on the plastically deformed connected portion without spoiling the compactness of the apparatus.
  • Fig. 1 shows a first embodiment of a bearing apparatus for a driving wheel of vehicle of the present invention.
  • the apparatus comprises a hub wheel 1, a double row rolling bearing 2 and a constant velocity universal joint 3 which are assembled as a unit.
  • a term "outboard side” of the apparatus denotes a side which is positioned outside of the vehicle body and a term “inboard side” of the apparatus denotes a side which is positioned inside of the body when the apparatus is mounted on the vehicle body.
  • the hub wheel 1 is formed integrally with a wheel mounting flange 4 at the outboard side of the hub wheel 1 on which a wheel (not shown) is mounted and hub bolts 4b are equidistantly arranged on the flange 4 along its periphery.
  • a wheel piloting portion 4a extends from the wheel mounting flange 4 to the outboard side.
  • the inner circumferential surface of the hub wheel 1 is formed with a irregular portion 5 which are heat treated as having a hardened layer 10 (shown by a cross-hatching in Fig. 1 ) having a surface hardness of HRC 54 - 64. It is preferable to use as heat treatment a high frequency induction heating which can easily carry out a local heating and a setting of the depth of a hardened layer.
  • Fig. 2 shows example of the irregular portion 5 in which Fig 2 (a) shows an example of the irregular portion 5 comprising mutually inclined helical grooves 6 and Fig.2 (b) shows another example of the irregular portion 5 of crossed grooves 6' comprising axial grooves and discontinuous annular grooves. It is preferable to form the irregular portion by pointed projections.
  • the double row rolling bearing 2 comprises an outer member 7, inner member 8 and a double row rolling elements 9 and 9.
  • the outer member 7 is integrally formed on its outer circumferential surface with a body mounting flange 7a and on its inner circumferential surface with double row outer raceway surfaces 7b and 7b.
  • the inner member 8 comprises the hub wheel 1 and an outer joint member 14 hereinafter described and inner raceway surfaces la and 14a opposed to the outer raceway surfaces 7b and 7b are arranged on the outer circumferential surfaces of the hub wheel 1 and the outer joint member 14 respectively.
  • the double row rolling elements 9 and 9 are contained between the outer raceway surfaces 7 b and 7b and the inner raceway surfaces 1a and 14a and freely rotatably held therein by cages 11 and 11. Seals 12 and 13 are arranged at the ends of the bearing 2 to prevent leak of grease contained within the bearing 2 as well as ingress of rain water or dusts.
  • the illustrated ball rolling elements 9 and 9 may be replaced for example by tapered rolling elements.
  • a hardened layer 10' (shown by a cross-hatching in Fig. 3 (a) ) is formed on the surface of the hub wheel 1 at a seal land portion 18 on which the seal 12 slidably contacts, the inner raceway surface 1a, a surface of spigot portion 1b against which a shoulder 16 of the outer joint member 14 abuts, and an end surface 19 of the spigot portion 1b.
  • the hardened layer 10' extends to the end surface 19 and partially to the inner circumferential surface of the end of the spigot portion 1b.
  • This arrangement enables to suppress abrasion of the spigot portion 1b and a stepped portion of small diameter 17a which are fitted with each other via a cylindrical surface.
  • a grease well 20 is formed on the inner surface of the end surface 19 of the spigot portion 1b.
  • the grease well 20 may be arranged on the inner circumferential surface of the spigot 1b.
  • the constant velocity universal joint comprises a joint inner ring, a cage and torque transmitting balls other than the outer joint member 14.
  • the outer joint member 14 has a cup-shaped mouth portion 15, a shoulder 16 forming the bottom of the mouth portion 15, a shaft portion 17 axially extending from the shoulder 16, and an axially extending curved track groove 15a formed on the inner surface of the mouth portion.
  • the outer joint member 14 is formed with the inner raceway surface 14a around the outer circumferential surface of the shoulder 16.
  • the shaft portion 17 of the outer joint member 14 has a stepped portion of small diameter 17a and a fitting portion 17b.
  • the fitting portion 17b is fitted into the hub wheel 1 with the end surface 19 of the spigot portion 1b of the hub wheel 1 being abutted against the shoulder 16 of the outer joint member 14.
  • the hub wheel 1 and the outer joint member 14 are integrally connected via plastic deformation of the fitting portion 17b of the outer joint member 14 with making the hardened irregular portion 5 of the hub wheel 1 to bite into the outer circumferential surface at the fitting portion of the outer joint member 14 by radially outwardly expanding the fitting portion of the outer joint member 14.
  • the caulking can be carried out, as shown in Figs. 4 (a) and (b) , firstly by placing the inner member 8 on a pedestal "B” and then by inserting a mandrel "M" into the outer joint member 14 from the inboard side to the outboard side. Since the spigot portion 1b of the hub wheel 1 is axially compressed between the shoulder 16 of the outer joint member 14 and the pedestal "B” and the fitting portion (cross-hatched portion) 17b is radially outwardly expanded, the residual compressive stress is still kept after the plastic deformed connection. Accordingly no axial clearance is caused at the abutted portion between the spigot portion 1b and shoulder 16 and thus the internal clearance of the double row rolling bearing 2 can be maintained at an initially set negative clearance.
  • the outer joint member 14 is formed with a hardened layer 10" at the track groove 15a formed on the inner surface of the mouth portion 15, and a region from the seal land portion 21 on which the seal slidably contacts to the stepped portion of small diameter 17a of the shaft portion 17 through the inner raceway surface 14a. It is preferable to carry out the heat treatment by the high frequency induction heating. It is also preferable to keep the fitting portion 17b as no-quenched portion having surface hardness less than HRC 24 and to set the surface hardness of the irregular portion 5 of the hub wheel 1 at about HRC 54 - 64 to hold a difference in the hardness between the irregular portion 5 and the fitting portion 17b larger than HRC 30. This enable the irregular portion 5 to easily bite into the fitting portion 17b without causing deformation of the irregular portion 5 to tightly combine them via the plastic deformation.
  • the abutted portion of the hub wheel 1 and the outer joint member 14 functions as a node and suffers from repeating bending moment when excessive bending moment arises during turning of a vehicle. During which, excessive stress tends to be caused at the spigot portion 1b of the hub wheel 1 and the shaft portion 17 of the outer joint member 14, especially at a corner 22 of the stepped portion of small diameter 17a and thus the durability would be reduced. In addition, abnormal abrasion would be caused in the abutted portion of the spigot portion 1b and the stepped portion of small diameter 17a due to their deformation or abraded debris would enter into the bearing.
  • the provision of the hardened layer 10" on the surface from the inner raceway surface 14a to the corner 22 enables to increase the strength and the durability against the torsional moment and also to suppress generation of abrasion even though relative slippage is caused by the repeating bending moment at the abutted portion between the spigot portion 1b and the shoulder 16.
  • an end cap is usually arranged at an end of the outer joint member 14 in order to prevent leakage of grease contained within the mouth portion 15 and ingress of dusts from the outside.
  • the spigot portion 1b of the hub wheel 1 and the stepped portion of small diameter 17a are fitted with each other via a cylindrical surface and thus sufficient rigidity can be obtained against the repeating bending load.
  • the radial clearance is set as small as possible according to the embodiment of the present invention at the sacrifice of easiness of assembly. It has been found that setting of the radial clearance in the fitting portion less than 0.5 mm is effective in improvement of the durability from a durability test carried out by the applicant.
  • Figs. 6 (a) and (b) are explanatory views each showing a stress caused when the bearing apparatus for a driving wheel suffered from the bending moment:
  • Fig. 6 (a) shows a case of an apparatus of the prior art, and
  • Fig. 6 (b) shows a case of the apparatus of the second embodiment of the present invention.
  • the bearing apparatus for a driving wheel in which the hub wheel 1 and the outer joint member 14 is integrated via plastic deformation, it is possible to reduce its manufacturing cost by reducing the length of the connection via plastic deformation because of possibility of reduction of working cost of the irregular portion 5 as well as the cycle time of the radially outward expanding step.
  • the applicant of the present invention has carried out an analysis of strength of several positions to find out an optimum relation between a length of the plastic deformation and its position, and a durability test when loaded by the bending moment by using various kinds of samples in which the length and position of the connection via plastic deformation are changed.
  • the area (L2) of pressure receiving surface for supporting the bending moment is larger than that (L1) in the apparatus of the prior art shown in Fig. 6 (a) . Accordingly, the stress (o2) caused in that area of the apparatus of the present invention is smaller than that (o1) of the prior art. Thus the durability of the bearing apparatus of the present invention can be extended than that of the prior art.
  • the reason why the durability of the bearing apparatus of the present invention is extended than that of the prior art is that the arrangement of the plastic deformed connection at an outboard side from the line of action of the bearing 2 enables suppress the action of the bending moment to the plastic deformed connection, and that the arrangement of the spigot fitting portion on the line of action increases its rigidity because of the bending moment being supported on the cylindrical surface of the spigot fitting portion.
  • smaller radial clearance in the spigot fitting portion is advantageous for suppressing the deformation of the hub wheel 1, it is set at 0,60 ⁇ -0.10mm, preferably at 0.35 ⁇ -0.05mm in view of easiness of fitting.
  • Fig. 7 is a longitudinal view showing another embodiment of the configuration of the irregular portion of the hub wheel of the present invention. Same reference numerals are also used in this drawing for designating same parts used in the first embodiment in Fig. 1 .
  • a plurality of parallel annular grooves 5a are firstly formed on the inner circumferential surface of a hub wheel 1' for example by turning as shown in Fig. 7 (a) .

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rolling Contact Bearings (AREA)

Claims (9)

  1. Lagervorrichtung für ein Antriebsrad eines Fahrzeugs, enthaltend ein Nabenrad (1), das an einem Ende mit einem Radanbringungsflansch (4) ausgebildet ist, ein Gleichlaufgelenk (3), das ein Gelenkaußenelement (14), das integral mit einem Öffnungsabschnitt (15), einem Schulterabschnitt (16), der die Unterseite des Öffnungsabschnittes (15) bildet, und einem Wellenabschnitt (17) ausgebildet ist, der sich axial von dem Schulterabschnitt (16) erstreckt, und ein Doppelreihenkugellager (2), das ein Fahrzeugrad im Bezug auf einen Fahrzeugkörper drehbar lagert, wobei das Nabenrad (1), das Gleichlaufgelenk (3) und das Doppelreihenkugellager (2) zu einer Einheit zusammengesetzt sind, eine der inneren Laufflächen (1a) auf der Außenumfangsfläche des Nabenrades (1) ausgebildet ist, die andere der inneren Laufflächen (14a) auf der Außenumfangsfläche des Gelenkaußenelementes (14) ausgebildet ist, das Nabenrad (1) und das Gelenkaußenelement (14) derart zusammengefügt sind, dass eine Stirnfläche an der Schulter des Gelenkaußenelementes (14) anliegt, die Innenumfangsfläche an dem Passabschnitt des Nabenrades (1) mit einem gehärteten unregelmäßigen Abschnitt (5) ausgebildet ist, und das Nabenrad (1) sowie das Gelenkaußenelement (14) über plastische Verformung des Gelenkaußenelementes (14) integral verbunden sind, indem der gehärtete unregelmäßige Abschnitt (5) in die Außenumfangsfläche an dem Passabschnitt des Gelenkaußenelementes (14) durch radiales nach außen Erweitern des Passabschnittes des Gelenkaußenelementes (14) beißt, dadurch gekennzeichnet, dass die Außenumfangsfläche des Gelenkaußenelementes (14) mit einer gehärteten Schicht (10") wenigstens in einem Bereich, der die innere Lauffläche (14a) und den Wellenabschnitt enthält, mit Ausnahme des Passabschnittes des Gelenkaußenelementes (14) ausgebildet ist.
  2. Lagervorrichtung nach Anspruch 1, bei der das Nabenrad (1) mit einem zylindrischen Zapfenabschnitt (1b) ausgebildet ist, der sich von der inneren Lauffläche (1a) axial erstreckt, und bei der eine gehärtete Schicht (10') auf der Außenumfangsfläche des Nabenrades (1) in einem Bereich ausgebildet ist, der den Zapfenabschnitt (1b) enthält und sich von der inneren Lauffläche (1a) zu einer Stirnfläche des Nabenrades (1) erstreckt.
  3. Lagervorrichtung nach Anspruch 2, bei der eine gehärtete Schicht (10) in einem Bereich des Nabenrades (1) ausgebildet ist, der sich von der Stirnfläche des Nabenrades (1) zur Innenumfangsfläche des Endes des Zapfenabschnittes (1b) erstreckt.
  4. Lagervorrichtung nach einem der Ansprüche 1 bis 3, bei der sich Schmierfett zwischen den Anlageflächen des Endes des Nabenrades (1) und der Schulter (16) des Gelenkaußenelementes befindet.
  5. Lagervorrichtung nach einem der Ansprüche 1 bis 4, bei der eine Schmierfettvertiefung auf der Stirnfläche des Nabenrades (1) ausgebildet ist.
  6. Lagervorrichtung nach einem der Ansprüche 2 bis 5, bei der der radiale Zwischenraum zwischen dem Zapfenabschnitt (1b) des Nabenrades (1) und dem Wellenabschnitt (17) des Gelenkaußenelementes (14) weniger als 0,5 mm beträgt.
  7. Lagervorrichtung nach einem der Ansprüche 1 bis 6, bei der der durch plastische Verformung verbundene Abschnitt axial außerhalb einer Wirkungslinie des Doppelreihenkugellagers (2) angeordnet ist.
  8. Lagervorrichtung nach Anspruch 7, bei der das Nabenrad (1) und das Gelenkaußenelement (14) wechselseitig durch einen Zapfen eingepasst sind, und bei der sich der Zapfenpassabschnitt auf der Wirkungslinie des Doppelreihenkugellagers (2) befindet.
  9. Lagervorrichtung nach Anspruch 7 oder 8, bei der sich das Nabenrad (1) nach außen von einem Radanbringungsflansch (4) erstreckt, um einen Radführungsabschnitt (4a) auszubilden, und bei der der durch plastische Verformung verbundene Abschnitt in einem Bereich von der Stirnfläche des Radführungsabschnittes (4a) zu dem Radanbringungsflansch (4) angeordnet ist.
EP02258836A 2001-12-21 2002-12-20 Lagervorrichtung für ein Antriebsrad eines Fahrzeuges Expired - Lifetime EP1321312B1 (de)

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
JP2001389630 2001-12-21
JP2001389630A JP4005354B2 (ja) 2001-12-21 2001-12-21 駆動車輪用軸受装置
JP2002000546 2002-01-07
JP2002000546A JP4071965B2 (ja) 2002-01-07 2002-01-07 駆動車輪用軸受装置
JP2002002673 2002-01-09
JP2002002673A JP2003206947A (ja) 2002-01-09 2002-01-09 駆動車輪用軸受装置

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EP1321312A2 EP1321312A2 (de) 2003-06-25
EP1321312A3 EP1321312A3 (de) 2005-03-16
EP1321312B1 true EP1321312B1 (de) 2010-09-15

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CN1426908A (zh) 2003-07-02
US7267490B2 (en) 2007-09-11
EP1321312A2 (de) 2003-06-25
US20030151223A1 (en) 2003-08-14
CN1315663C (zh) 2007-05-16
KR20030053032A (ko) 2003-06-27
DE60237669D1 (de) 2010-10-28

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